JP2007132435A - Disk brake device - Google Patents

Abstract

<P>PROBLEM TO BE SOLVED: To provide a disk brake device movable so as not to incline a pad back plate and a frictional material supported by the pad back plate up to generating braking force by contact of both by moving the pad back plate toward a disk rotor while restraining vibration in non-brake operation. <P>SOLUTION: An imparting position of pressing force imparted to a guide part 30 by a leaf spring 34 and a pressure receiving position of reaction received from a torque receiving groove 32 to the guide part 30 by the pressing force by the leaf spring 34, are determined on an equal distance from the pressing center O of a pressing cylinder part. The imparting position of the pressing force and the pressure receiving position of the reaction exist at the equal distance from the pressing center O, and since sliding resistance force generated there is equal, when pressing the pad back plate 22 by the cylinder part, the pad back plate 22 can be moved toward the disk rotor without inclining. <P>COPYRIGHT: (C)2007,JPO&INPIT

Description

  The present invention relates to an improvement in a pad backing metal that supports a friction material of a disk brake device, particularly a disk brake device.

  As one of braking devices for braking a vehicle, there is a disc brake device. This disc brake is composed of a disc rotor and a caliper that rotate together with the wheels. The caliper has a housing portion that forms an outer shape and functions as a cylinder, and a mount that includes a torque receiving surface that fixes the caliper itself to the vehicle body and receives braking torque generated during braking. The housing portion includes a piston, and includes a pair of friction materials arranged with a disc rotor interposed therebetween, and a pair of pad backing plates that respectively support the friction materials. For example, convex guide portions are formed at both ends of the pad back metal, and the pad back metal is supported by the mount by engaging with a groove forming a torque receiving surface of the mount. In the disc brake device having such a configuration, when hydraulic pressure is introduced between the housing portion and the piston, the guide portion slides in the groove and moves to the disc rotor side, and the friction material is pressed against the disc rotor to thereby apply a braking force. Can be generated.

  The friction material has, for example, a fan shape, and the pad back metal has, for example, substantially the same shape or a rectangular shape so as to support the friction material. The friction material is dragged by the disk rotor while coming into contact with the disk rotor at the time of braking and is dragged by the disk rotor.For example, when traveling forward, a tangential force is generated forward, and this tangential force is transmitted through the guide portion of the pad back metal. Acts on the torque receiving surface of the mount. The pad back metal is pressed against the torque receiving surface by a tangential force generated by the braking torque of the friction material at the same time as it moves toward the disk rotor by the cylinder.

By the way, at the time of non-braking operation, the pad back metal and the friction material are retracted in a direction away from the disk rotor, and are moved toward the disk rotor at the time of braking operation. For example, in the disc brake disclosed in Patent Document 1, the pad back metal is supported in a loosely fitted state on the mount so that the movement at this time can be performed smoothly. With this configuration, the sliding resistance between the guide portion and the mount is reduced during the movement of the pad back metal, and the movement can be performed smoothly. Further, in the disc brake device disclosed in Patent Document 2, a state in which the pad back metal is lifted from the mount by an anti-rattle spring during non-brake operation is created, and the sliding resistance between the pad back metal and the mount is reduced. As a result, the pad backing metal can be easily moved.
JP 2005-121051 A JP-A-8-254232

  However, in the case of the structure of Patent Document 1, since the pad back metal is supported in a loosely fitted state on the mount, there is a problem that the pad back metal vibrates and comes into contact with the mount during non-brake operation. There is. In the case of the structure of Patent Document 2, since the pad back metal is pressed against the mount by the anti-rattle spring, vibration during non-braking operation can be reduced, but the sliding frictional force based on the pressing force by the anti-rattle spring and its pressing force Since there is no consideration for the sliding frictional force based on the reaction force generated against the above, there is a problem that the pad backing metal is inclined in the rotation direction of the disk rotor and the thickness direction of the pad backing metal when the pad backing metal is moved. When the pad back metal is tilted, the friction material and the disc rotor come into contact with each other in this posture, which causes uneven wear of the friction material.

  The present invention has been made in view of such a situation, and its purpose is to suppress the vibration during non-braking operation and move the pad back metal toward the disk rotor until a braking force is generated by contact between the two. Meanwhile, an object of the present invention is to provide a disc brake device that can be moved while preventing the pad backing metal and the friction material supported by the pad backing metal from tilting.

  In order to solve the above-described problems, a disc brake device according to the present invention includes a friction material disposed to face a friction sliding surface of a disc rotor that rotates with a wheel, and a surface of the friction material that does not face the disc rotor. A pad backing plate having a supporting surface to be supported and having a pair of guide portions on both end surfaces of the supporting surface; and pressing the non-supporting surface of the pad backing plate in a direction substantially parallel to the rotational axis of the disk rotor. The pressing means for pressing the friction material against the friction sliding surface of the disk rotor, and the pad backing metal guide portion being engaged, allowing the pad backing metal to move toward the disk rotor, and the pad Torque receiving to receive the braking torque generated in the friction material when the back metal is pressed by the pressing means and the friction material comes into contact with the disk rotor and generates a braking force. A vehicle body fixing mount having a surface; and a pressing member that presses a part of the guide portion and presses the guide portion against the torque receiving surface, and the pressing force applied to the guide portion by the pressing member The pressure receiving position of the reaction force received by the guide portion from the torque receiving surface due to the pressing force by the pressing member is determined at an equal distance from the pressing center position of the pressing means.

  According to this aspect, since the pad backing metal is pressed against the torque receiving surface by the pressing member, the vibration of the pad backing metal is suppressed when the friction material and the disk rotor are not in contact. In addition, the position where the pressing force is applied by the pressing means and the pressure receiving position of the reaction force are set at the same distance from the pressing center position of the pressing means, so that the sliding generated based on the pressing force and the reaction force when the pad back metal is moved. Dynamic friction force is equal. As a result, the pad backing metal can be moved without being tilted by the pressing of the pressing means. That is, it becomes possible to press the friction material in a posture in which the inclination is reduced with respect to the disk rotor, and uneven wear of the friction material can be suppressed. Even when the pad back metal is tilted from the beginning, the posture of the pad back metal is corrected by the reaction force received from the disk rotor when the friction material contacts the disk rotor, and the friction material and the disk rotor contact in parallel. It becomes like this. As a result, even if the pad backing metal moves while being tilted, uneven wear of the friction material can be suppressed. Further, since the inclination of the pad backing metal, that is, the friction material with respect to the disk rotor is reduced, so-called brake squealing can be reduced.

  Further, in the above aspect, the pressing member is a side pressing member that presses at least one end face of the guide portion, and a pressing force applying position that the side pressing member applies to the guide portion, and the side pressing member. The pressure receiving position of the reaction force received by the other guide portion from the torque receiving surface by the pressing force of may be determined at an equal distance from the pressing center position of the pressing means. According to this aspect, it can suppress that a pad back metal inclines with respect to the exit / entry direction of a disk rotor.

  In the above aspect, the pressing member is a vertical pressing member that presses at least one surface of the upper surface or the lower surface of each guide portion, and the vertical pressing member is at least one surface of the upper surface or the lower surface of the guide portion. The pressure application position to which the other surface of the guide portion receives from the torque receiving surface by the pressing force of the upper and lower pressing members is determined at an equal distance from the pressing center position of the pressing means. It may be. According to this aspect, it is possible to suppress the pad backing metal from being inclined with respect to the inner and outer peripheral directions of the disk rotor.

  Further, in the above aspect, the pressing member is a side pressing member that presses at least one end surface of the guide portion, and a vertical pressing member that presses at least one surface of the upper surface or the lower surface of each guide portion, Position for applying a pressing force applied by the side pressing member and the vertical pressing member to the guide portion, and a pressure receiving position for a reaction force received by the guide portion from the torque receiving surface by the pressing force of the side pressing member and the vertical pressing member May be set at an equal distance from the pressing center position of the pressing means. According to this aspect, it can suppress that a pad back metal inclines with respect to both the entrance / exit direction of a disc rotor, and an inner-outer peripheral direction.

  According to the disc brake device of the present invention, it is possible to press the pad back metal in a posture with reduced inclination with respect to the disc rotor while suppressing vibration when the disc brake device is not operated, thereby reducing uneven wear.

  Hereinafter, an embodiment of the present invention (hereinafter referred to as an embodiment) will be described with reference to the drawings.

  The caliper of the disc brake device according to the present embodiment includes a friction material, a pad backing metal having a pair of guide portions, a pressing means, a vehicle body fixing mount, and a guide portion. And a pressing member that presses the portion. The pressing member presses the guide portion against the torque receiving surface. At this time, the application position of the pressing force applied by the pressing member to the guide portion and the pressure receiving position of the reaction force received by the guide portion from the torque receiving surface by the pressing force of the pressing member are determined at an equal distance from the pressing center position of the pressing means. It has been. Since the pressing force application position and the reaction force receiving position are equidistant from the pressing center position of the pressing means, and the sliding resistance force generated there is also equal, when pressing the pad back metal with the pressing means, the pad back metal is not inclined. Can be moved.

  FIG. 1 is a side view of a floating caliper 10 constituting the disc brake device of the present embodiment, and FIG. 2 is a sectional view taken along line AA in FIG. FIG. 3 is a cross-sectional view taken along line BB in FIG. As shown in FIG. 1, the caliper 10 according to the present embodiment is roughly divided into a vehicle body fixing mount (mounting) 12 for fixing the caliper itself to a vehicle body (not shown), and a brake pad that is pressed by the disk rotor to generate a braking force. 14 and a cylinder portion 16 that functions as a pressing means for driving the brake pad 14. As shown in FIG. 2, the disk rotor 18 that rotates together with the wheels exists between the pair of brake pads 14. The side surfaces 18 a and 18 b of the disk rotor 18 constitute a friction sliding surface, and a pair of brake pads 14 are disposed opposite to each other with the disk rotor 18 interposed therebetween. The brake pad 14 includes a friction material 20 that directly contacts the side surfaces 18 a and 18 b of the disk rotor 18, and a pad back metal 22 that supports the back side of the friction material 20, that is, the side that does not contact the disk rotor 18.

  The caliper 10 is attached to the vehicle body via a vehicle body fixing mount 12 so as to be displaceable in the left-right direction in FIG. As shown in FIG. 2, a bottomed hole 24 is formed in the cylinder portion 16 of the caliper 10, and a piston 26 is slidably fitted into the hole 24. A port (not shown) is provided at the bottom of the hole 24 and is connected to a master cylinder (not shown) via a hydraulic pipe. When the driver operates the brake pedal, the brake oil from the master cylinder flows into the port and drives the piston 26.

  When the brake oil flows into the port, the piston 26 slides from the non-operating state shown in FIG. 2 in the direction of the arrow R, that is, the pressing direction of the piston 26, and the friction material 20a is moved to the side surface of the disk rotor 18 via the pad back metal 22a. Press to 18a. When the friction material 20a is pressed against the disk rotor 18, the piston 26 stops sliding. Even after the piston 26 stops sliding, if the brake oil flows into the port, the hydraulic pressure in the hole 24 further increases. As a result, the stopped piston 26 reversely presses the inner surface of the hole 24, presses the cylinder housing 16a constituting the cylinder portion 16 in the direction of the arrow L, that is, in the reverse direction of the arrow R, and as the hydraulic pressure increases, The cylinder housing 16a is displaced in the arrow L direction.

  A claw portion 28 is formed on the non-cylinder forming side of the cylinder housing 16a. As the cylinder housing 16a is displaced in the direction of arrow L, the claw portion 28 causes the friction material 20b to pass through the pad back metal 22b to the disc rotor 18. Is pressed against the side surface 18b. Therefore, the disk rotor 18 is pressed and clamped by the pair of friction materials 20a and 20b, and the disk rotor 18 can be braked efficiently.

  As shown in FIG. 3, the pad backing metal 22 a that supports the friction material 20 a has a pair of guide portions 30 that are formed on both end surfaces of the friction material 20 a of the pad backing metal 22 a and have a predetermined vertical width P. ing. This guide portion 30 is engaged with a torque receiving groove 32 functioning as a torque receiving surface formed on the vehicle body fixed mount 12 side in a loosely fitted state. When the friction material 20 a is brought into contact with the rotating disk rotor 18, the friction material 20 a is dragged by the disk rotor 18 and receives a tangential force in the tangential direction with respect to the disk rotor 18, that is, braking torque. This tangential force is received by the torque receiving groove 32 of the vehicle body fixing mount 12 through the pad back metal 22a. In other words, the torque receiving groove 32 contacts the end surface portion of the pad backing metal 22a on the outlet side of the friction material 20a with respect to the rotation direction of the disk rotor 18 when the pad backing metal 22a is pressed, and receives the tangential force of the friction material 20a. For example, in FIG. 3, when the disk rotor 18 (not shown) rotates counterclockwise, the torque receiving groove 32a receives the braking torque of the guide portion 30 that engages with the torque receiving groove 32a. Conversely, when the disk rotor 18 (not shown) rotates in the clockwise direction, the torque receiving groove 32b receives the braking torque of the guide portion 30 that engages with the torque receiving groove 32b. As a result, a good braking force can be ensured both when the vehicle is moving forward and when the vehicle is moving backward.

  By the way, the pad backing metal 22 that supports the friction material 20 is retracted to a position away from the disk rotor 18 during non-braking operation. When brake oil is introduced into the cylinder portion 16, the pad back metal 22 starts moving toward the disc rotor 18. In order to perform this movement smoothly, the guide portion 30 and the torque receiving groove 32 are engaged in a loosely fitted state. However, in a completely loose-fitted state in which a clearance is formed, the pad back metal 22 vibrates and generates abnormal noise when the vehicle is running. Therefore, a leaf spring 34 is inserted as a pressing means between the pad back metal 22 and the torque receiving groove 32 of the present embodiment. By inserting the leaf spring 34, the pad back metal 22 can be moved smoothly while filling the clearance.

  FIG. 4 shows an example of the leaf spring 34. The leaf spring 34 in this example has a side pressing function for pressing the end surface of the guide portion 30 of the pad back metal 22 and a lower surface pressing function for pressing the lower surface of the guide portion 30. That is, the leaf spring 34 has a side pressing piece 34a that functions as a side pressing member that generates a side pressing force in the direction of arrow S in the drawing, and a lower surface that functions as a vertical pressing member that generates a lower surface pressing force in the direction of arrow U. And a pressing piece 34b. In order to attach the leaf spring 34 to the guide portion 30, a support piece 34c is formed on the opposite surface of the lower surface pressing piece 34b. The leaf spring 34 can be formed of, for example, a well-known spring steel material. In the embodiment described below, it is assumed that the sliding friction coefficients between the leaf springs 34 attached to the left and right guide portions 30 of the pad back metal 22 and the torque receiving grooves 32 are the same.

  FIG. 5 shows a state in which the leaf spring 34 is attached to the guide portion 30. In this manner, the pad back metal 22 is urged by the opposite side torque receiving groove 32 by the side pushing piece 34 a of the leaf spring 34. Further, the pad backing metal 22 is urged toward the upper surface side of the torque receiving groove 32 by the lower surface pressing piece 34b. As a result, even when the disc brake device is in a non-brake operation state, the pad backing metal 22 is urged to the torque receiving groove 32, and the pad backing metal 22 is prevented from vibrating inside the torque receiving groove 32. Since the pad back metal 22 has the guide portions 30 at both ends, the leaf spring 34 shown in FIG. For the purpose of preventing vibration, the pad backing metal 22 only needs to be urged by the torque receiving groove 32, and therefore it is not necessary to push both guide portions 30 side by side. When the side push is performed only on one guide portion 30, the leaf spring 34 shown in FIG. 4 is attached to the one guide portion 30, and the leaf spring from which the side push piece 34a is removed may be attached to the other guide portion 30. Moreover, although the leaf spring 34 of FIG. 4 has shown the structure which urges | biass a lower surface by the lower surface pressing piece 34b, you may form the upper surface pressing piece which presses an upper surface. Moreover, you may provide the lower surface pushing piece 34b and the upper surface pushing piece. Further, a leaf spring that performs only side pushing, a leaf spring that biases only the lower surface, a leaf spring that biases only the upper surface, or a leaf spring that biases only the upper and lower surfaces may be employed.

  In the present embodiment, when the leaf spring 34 is attached to the guide portion 30, the guide portion 30 is applied to the torque receiving groove 32 by the application position of the pressing force applied by the leaf spring 34 to the guide portion 30 and the pressing force by the leaf spring 34. The pressure receiving position of the reaction force received from is determined at an equal distance from the pressing center position of the cylinder portion 16.

  FIG. 6 shows a case where only the side push by the leaf spring 34 is performed. The leaf spring 34 having only the side pushing piece 34 a is attached to one guide portion 30 of the pad back metal 22. In this case, the other guide portion 30 receives the reaction force S2 from the torque receiving groove 32 by the pressing force S1 of the side pressing piece 34a. In this state, when the pad backing metal 22 is moved toward the disk rotor 18, a sliding frictional force based on the pressing force S1 and the reaction force S2 is generated. As described above, in the present embodiment, the position where the pressing force S1 is applied and the pressure receiving position where the reaction force S2 is received are determined to be equidistant from the pressing center position of the pressing means. That is, the distances L1 and L2 from the pressing center O of the cylinder portion 16 are determined to be the same. Therefore, the sliding frictional force generated between the guide portion 30 and the torque receiving groove 32 when the pad backing metal 22 is moved becomes equal. As a result, if the cylinder portion 16 is designed so as to push the pad back metal 22 in a direction substantially parallel to the rotation axis of the disk rotor 18, the pad back metal 22 moves in the left-right direction (disc It moves toward the disc rotor 18 without tilting in the direction in which the rotor 18 enters and exits. As a result, the friction material 20 comes into contact with the disk rotor 18 without tilting left and right, and begins to generate a braking force. That is, uneven wear of the friction material 20 in the left-right direction (the direction in which the disk rotor 18 enters and exits) can be suppressed. In addition, although the guide part 30 and the torque receiving groove 32 are actually in a surface contact state, in the description of the present embodiment, the center of gravity position of the surface contact area is illustrated as the application position and the pressure receiving position for convenience.

  In the above description, the one side guide piece 30 is set as the pressing side and the other side as the pressure receiving side by the side pressing piece 34 a, but the side pressing pieces 34 a may be attached to both guide parts 30. In this case, it is only necessary that the center O of the cylinder portion 16 be equidistant with respect to the resultant force of the pressing force and the reaction force, and the same effect can be obtained.

  FIG. 7 shows a case where only the lower surface pressing by the leaf spring 34 is performed. A leaf spring 34 having only a lower surface pressing piece 34 b is attached to both guide portions 30 of the pad back metal 22. In this case, the reaction force U2 is received from the upper surface side of the torque receiving groove 32 by the pressing force U1 of the lower surface pressing piece 34b. In this state, when the pad backing metal 22 is moved toward the disk rotor 18, a sliding frictional force based on the pressing force U1 and reaction force U2 is generated. As described above, in this embodiment, the application position of the pressing force U1 and the pressure receiving position of the reaction force U2 are determined to be equidistant from the pressing center position of the pressing means. That is, the distances L3 and L4 from the pressing center O of the cylinder portion 16 are determined to be the same. Therefore, the sliding frictional force generated between the guide portion 30 and the torque receiving groove 32 when the pad backing metal 22 is moved becomes equal. As a result, if the cylinder portion 16 is designed so as to push the pad back metal 22 in a direction substantially parallel to the rotational axis of the disk rotor 18, the pad back metal 22 is moved in the vertical direction (disc It moves toward the disk rotor 18 without tilting in the direction of the inner and outer circumferences of the rotor 18. As a result, the friction material 20 comes into contact with the disk rotor 18 without tilting in the vertical direction and starts to generate a braking force. That is, uneven wear in the vertical direction of the friction material 20 can be suppressed. In this case as well, the guide portion 30 and the torque receiving groove 32 are actually in a surface contact state, but in the description of the present embodiment, the center of gravity position of the surface contact region is illustrated as an applied position and a pressure receiving position for convenience. ing. In the above-described example, the leaf spring 34 having only the lower surface pressing piece 34b is described. However, the same effect can be obtained in the case of the leaf spring having only the upper surface pressing piece. Further, in the case of the leaf spring having the lower surface pressing piece 34b and the upper surface pressing piece, the pressing center O of the cylinder portion 16 may be equidistant with respect to the resultant force of the pressing force and the reaction force, and the same effect is obtained. be able to.

  In this way, the application position of the pressing force applied to the guide portion 30 and the pressure receiving position of the reaction force received by the guide portion 30 from the torque receiving groove 32 by this pressing force are set equal to the pressing center position of the cylinder portion 16. As a result, vibrations and abnormal noises during non-braking operations can be suppressed, and tilting of the posture during movement of the pad back metal 22 can be reduced. Further, since the inclination of the pad back metal 22 is reduced, so-called brake squealing is also reduced.

  6 and 7, the side pressing state and the bottom surface pressing state have been described separately. However, with the leaf spring 34 shown in FIG. 4, with respect to the side pressing and the bottom surface pressing, a pressing force applying position and a reaction force receiving position are used. Are set to be equidistant with respect to the position of the pressing center O of the cylinder portion 16, both the horizontal inclination and the vertical inclination of the pad back metal 22 can be prevented. That is, when the pad back metal 22 is moved to the disk rotor 18, the friction surface of the friction material 20 can be brought close to the friction sliding surface of the disk rotor 18 in a substantially parallel posture. As a result, uneven wear of the friction material 20 can be suppressed both in the direction in which the disk rotor 18 enters and exits and in the inner and outer peripheral directions, and the occurrence rate of uneven wear of the friction material 20 is greatly reduced.

  In the case of the caliper 10, the pad back metal 22 may already be tilted for non-braking operation due to the tilt of the vehicle and wheels and the weight of the cylinder portion 16. When the positional relationship between the applying position, the pressure receiving position, and the pressing center O is formed as described above, the pad back metal 22 moves while maintaining the posture at the start of movement with respect to the pressing of the cylinder portion 16, so that it tilts from the beginning. In this case, the friction material 20 supported by the pad back metal 22 contacts the disk rotor 18 while being inclined. However, since the sliding frictional force generated at the applying position and the pressure receiving position is equal, the pad back metal 22 itself easily rotates due to the reaction force received by the portion of the friction material 20 that is inclined and first contacts the disk rotor 18. Thus, the posture of the pad back metal 22 is corrected so as to follow the sliding surface of the disk rotor 18. As a result, the friction material 20 becomes parallel to the disk rotor 18 until the braking force actually starts to be generated, and uneven wear can be suppressed.

  In the above-described example, the pad backing metal 22a on the cylinder portion 16 side has been described. However, the same configuration can be applied to the pad backing metal 22b on the opposite side of the disk rotor 18, and similar effects can be obtained. . The pad backing metal 22b on the opposite side of the disk rotor 18 is pressed by the claw portion 28 as described above. Therefore, each positional relationship may be determined so that the position where the pressing force is applied by the leaf spring 34 in the guide portion 30 and the pressure receiving position of the reaction force are equidistant from the center of pressing by the claw portion 28.

  The shape of the caliper 10 shown in FIG. 1 to FIG. 3 is an example, so that the pressing force applying position by a pressing member, for example, a leaf spring, and the reaction pressure receiving position are equidistant from the pressing center by the pressing means. Each positional relationship only needs to be defined, and other configurations and shapes can be arbitrarily changed, and the same effects as in the present embodiment can be obtained.

  In the present embodiment, the floating type is shown as an example of the caliper of the disc brake device. However, the configuration of the present embodiment is also applied to a fixed caliper that presses the pad back metal on both sides of the disc rotor with dedicated pistons. It is possible and the same effect can be obtained. In the present embodiment, the guide portion has a convex shape and the torque receiving surface has a groove shape. However, the guide portion side may have a concave shape, and the torque receiving side may have a convex shape. Obtainable.

  The present invention is not limited to the above-described embodiments, and various modifications such as design changes can be added based on the knowledge of those skilled in the art. The configuration shown in each figure is for explaining an example, and any configuration that can achieve the same function can be changed as appropriate, and the same effect can be obtained.

It is a side view of the caliper of the disc brake device concerning this embodiment. It is sectional drawing in line segment AA of FIG. It is sectional drawing in line segment BB of FIG. It is a perspective view of the leaf spring which is an example of the press member used for this embodiment. FIG. 5 is an explanatory diagram for explaining a state in which the leaf spring of FIG. 4 is mounted on a pad back metal. In this embodiment, it is explanatory drawing explaining the relationship between the provision position of the pressing force at the time of side pressing, the pressure receiving position of the reaction force, and the pressing center of a cylinder part. In this embodiment, it is explanatory drawing explaining the relationship between the provision position of the pressing force at the time of lower surface pressing, the pressure receiving position of the reaction force, and the pressing center of a cylinder part.

Explanation of symbols

  DESCRIPTION OF SYMBOLS 10 Caliper, 12 Car body fixed mount, 14 Brake pad, 16 Cylinder part, 16a Cylinder housing, 18 Disc rotor, 20 Friction material, 22 Pad back metal, 24 Hole, 26 Piston, 28 Claw part, 30 Guide part, 32 Torque receiving groove 34 leaf spring, 34a side pressing piece, 34b bottom pressing piece, 34c support piece.

Claims (4)

A friction material disposed opposite to the friction sliding surface of the disk rotor rotating with the wheel;
A pad backing plate having a support surface for supporting a surface of the friction material that does not face the disk rotor, and having a pair of guide portions on both end surfaces of the support surface;
A pressing means for pressing the non-supporting surface of the pad backing metal in a direction substantially parallel to the rotation axis of the disk rotor, and pressing the friction material against the friction sliding surface of the disk rotor;
The pad backing metal is allowed to move toward the disk rotor by engaging with the guide part of the pad backing metal, and the pad backing metal is pressed by the pressing means so that the friction material contacts the disk rotor. A vehicle body fixing mount having a torque receiving surface for receiving a braking torque generated in the friction material when a braking force is generated;
A pressing member that presses a part of the guide part and presses the guide part against the torque receiving surface;
Including
The pressing force applying position applied by the pressing member to the guide portion and the pressure receiving position of the reaction force received by the guide portion from the torque receiving surface by the pressing force by the pressing member are equidistant from the pressing center position of the pressing means. A disc brake device characterized by being defined. The pressing member is a side pressing member that presses at least one end face of the guide portion,
The pressing position of the pressing force applied to the guide part by the side pressing member and the pressure receiving position of the reaction force received from the torque receiving surface by the other guide part by the pressing force of the side pressing member are the pressing center position of the pressing means. The disc brake device according to claim 1, wherein the disc brake device is set at an equal distance from the center. The pressing member is a vertical pressing member that presses at least one surface of the upper surface or the lower surface of each guide portion,
The position of the pressing force applied by the vertical pressing member to at least one surface of the upper surface or the lower surface of the guide portion, and the reaction force that the other surface of the guide portion receives from the torque receiving surface by the pressing force of the vertical pressing member. 2. The disc brake device according to claim 1, wherein the pressure receiving position is set at an equal distance from the pressing center position of the pressing means. The pressing member is a side pressing member that presses at least one end surface of the guide portion, and a vertical pressing member that presses at least one surface of the upper surface or the lower surface of each guide portion,
Position for applying a pressing force applied by the side pressing member and the vertical pressing member to the guide portion, and a pressure receiving position for a reaction force received by the guide portion from the torque receiving surface by the pressing force of the side pressing member and the vertical pressing member 2. The disc brake device according to claim 1, wherein each of the disc brake devices is set at an equal distance from a pressing center position of the pressing means.

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